Turbodrive control



July 31, o SCHJOLIN TURBO DRIVE CONTROL Filed Oct. 16,- 1 939 7 Sheets-Sheet l Smacntor (Ittomegs July 31, 19515. H. o. SCHJOLIN TURBO DRIVE CONTROL Filed 001;. 16, 1939 7 Sheets-Sheet 2 Enventor 2221/5 aic blziz r attorneys July 31, 1945. H. o. SCHJOLIN TURBO DRIVE CO NTROL Filed Oct. 16, 1939 7 Sheets-Sheet 4 I is nnenior fills (Q 50/;[0/112 July 31, 1945.

H. o. SCHJOLIN TURBO DRIVE CONTROL Filed Oct. 16, 1959 7 Sheets-Sheet 5 Ehwentor @2211: Q 52/1 01:

attorneys July 31, 1945. H. o. SCHJOLIN TURBO DRIVE CONTROL 7 Sheets-$heet 6 Filed Oct. 16, 1959 I 3112mm: 9/4275 Q fai /011a MW attorneys July 31, 1945. H. o. SCHJOLIN TURBO DRIVE CONTROL Filed Oct. 16, 1959 7 Sheets-Sheet '7 l'mn entor 92211.5 (Q 5647/0/13 I (Ittoxnegs Patented July 31, 1945 UNITED STATES PATENT 2,380,877 TUBBODBIVE CONTROL Hans o. Schjolin, Pontiac, Mich asslgnor, by

mesne assignments, to General Motors Corporation, Detroit, Mich, a corporation or Delaware Application October 16, 1939, Serial No. 299,643

, 18 Claims.

The invention relates to motor vehicles, more particularly of the type in which the driver's station may be located at some distancefrom the power plant. It relates specifically to automatic,

remotely operated controls for the speed ratiodriving mechanism, whereby the vehicle operator retains complete mastery of the mechanism, while permitting certain automatic control functions to be carried on. It relates to interruptive devices whereby the operator may definitely compelforms of operation which would otherwise be sell actuating in the automatic sense; and to force amplllying means for carrying out both automatic and manual control actions, such as is providedby power servo means. a

The invention relates to vehicle power plant installations which aflford a range ofinflnitely trol being operated by the auxiliary power utilized to actuate the said shift. An associated object is to provide a throttle restoring action, likewise operated by the auxiliary power shift means.

A further object is to provide an interlocking control between the selector for forward and reverse drive, and the automatically operated mechanism, effective to place the driving means for the direct and the infinitely variable drive in neutral condition prior to a selection by said selector,

and to afford therein an auxiliary neutral compelling means for emerge cy use.

An additional object is to provide a control worked by the engine accelerator pedal eflective at beyond full throttle position to actuate the ratio shift mechanism, to establish reduction drive by the infinitely variable driving means, while renmeans for the pluralspeed ratio determining means of-the driving mechanism, and subject to the automat'c and manual controls above referred The principal object or the invention is to providean automatically operated, but manually dominated vehicle drive embodying direct and in-i which enable the .vehicle operator to select the desired operating conditions through relay mechanisms eifective to compel drive actuation by unitary auxiliary power means.

An additional object is to provide a dual clutch drive capable of alternate actuation and of alternate loading by a single loading means, and adapted to be operated by the unitary auxiliary power means noted above.

Among the objects is that of providing a manual control to be preset for all forward drive, and operated normally thereafter by'automatic ratio selection means except for interruption by manual 'controls which can compel the actuating means to establish speed ratio control regimes other than automatically chosen, and which can com el drive indefinitely in a given speed ratio range.

In the present example, a drive for a large passenger vehicle is shown, with dual friction clutches loaded by a single loading means eflective in one of two positions to establish drive in direct between the vehicle engine and the final drive, and effective in the other position to establish an infinitely variable speed ratio range therebetween. The dual clutches are operated by a single air pressure servo piston and cylinder, the master valve therefor being controlled by electrical circuits, the switchesof which are governor,

and manually controlled. Auxiliary switches are operated by the engine accelerator pedal, and by the forward-and-reverse gearshift lever, as well by separate dash control, for purposes to be describedherein in full.

as The control system herein taught and the ratio actuation means responding to the controls are believed novel, and of utility in the art of vehicle drive operation.

Figure 1 is a schematic view orthe invention as applied to ,a motor bus, with the power plant arranged transversely at the rear, with the operator's control station located at the far end of the vehicle.

Figure 2 is a longitudinal section of the primary '45 driving assembly taken in a longitudinal plane of dering the automatic selection of drive ineffective.

.Another object is to provide a single actuating Figure 1.

Figure 3 is a section at 3-4 of Figur 2showing the details of the dual clutch construction thereoi.

Figure 4 is asectional view hr the servo actuatfinitely variable drive means. the controls or so with auxiliary throttlecontrol means.

Figure 8 is a sectional view of the solenoid valve controlling the movement oi the structures of Figures 4 to '7 inclusive.

Figure 9 is a schematic diagram of a control system for the structures of Figures 4 to 8, operated by governor G, and adapted to exert a reactive effect upon the engine throttle, but arranged to accomplish this act without interfering with the operators use of the accelerator pedal, by reason of the lost motion connection in the throttle rodding.

Figure 10 is a vertical view, in part section. of the mechanism in the driver's compartment for controlling the reverse-forward shift rod Ill of Figure 1, and for compelling the mechanism of Figure 4 to shift to, and remain in neutral position. Figure 11 is a sectional view at ll-H of Figure 10 showing the means for locking out the motion of the gear lever of Figure 10.

Figure 10a is a partial section of a portion of switch I? shown in Figure 10.

Figures 12 and 12a illustrate the neutral lock means controlled by the structure of Figure 10 in part, for compelling the Figure 4 construction to shift to, and remain in neutral. Figure 13 is a detail of the construction of certain of the parts of Figure 12.

Figure 14 is a schematic control diagram, similar to that of Figure 9, but showing the arrangement of the control elements of Figures 10 to 13, for the neutral shift mechanism above referred to.

Figure 15 is a further schematic control diagram similar to Figures 9 and 14, but representing a modification in which the operator's accelerator pedal is arranged to compel a downshift from direct to torque converter drive, when the pedal is moved beyond full throttle position.

Figures 16 and 17 are provided to show a specific version of the interlocking controls involving the master selector of drive, manually operated, and the mechanism operated by the driver's accelerator pedal, in determining the drive of the vehicle.

Figure 16 is a perspective view of a forward, neutral and reverse selector arranged to control rodding as shown in Figure 1,-and likewise to control a switch directing the energising current for the fluid pressure system actuating the drive' of the Figure 2 disclosure through the means described in conjunction with Figures 4 to 9 inclusive.

Figure 17 is a schematic diagram of the control system of the invention as applied to a Dieselengine-equipped drive. This flgure is equivalent to the combination of Figures 14 and 15, but the showing embraces the modification of Figure 16 rather than that of Figure 10, with respect to the manual selector for forward, neutral and reverse.

The general construction of the drive arrangement of Figure 2 follows that of Figures 2 and of my United States Serial Number 189,596, filed February 9, 1938, in which two friction clutches C and D are displaced at either end of the transmission, the first for coupling the torque converter T to the engine, and the other for coupling the engine directly to the final drive.

In my United States Serial Number 225,860, filed August 20, 1938, isshown a rearrangement of the friction clutches C and D. in Figures 6 and 7 thereof, the two friction clutches being grouped together adjacent the engine, with the torque converter T at the far end of the casing, the drive to the vehicle wheels being taken out on the main shaft center-line by ri ht-angle gearingto the final drive shaft ll. This latter arrangement is similar to that of the present demonstration.

The double-clutch construction is particularly arranged so that only one loading system sumces for both clutches, and further, a unitary mechanical linkage operates both clutches. The invention embodies actuation of this linkage, and thereby, the said clutches, from one single servo piston in a single cylinder.

In Figure 1 the drive arrangement is shown as installed in the rear of a passenger bus, the primary power plant arranged transversely and the output drive in the fore-and-aft direction of the vehicle connected by a iaekshaft to the conventional differential gear and axle drive to the rear-wheels.

The primary power plant comprises an engine A, in the present example of Diesel type, a fluid turbine type of torque converter T used as a variable speed transmission, a clutch C for coupling the turbine to the engine, a clutch D for coupling the engine directly to the final drive; an overrunning device F for disconnecting the turbine from the load shaft, when the clutch D is driving, and a gear assembly R for connecting the forward and reverse drives from neutral.

The propeller shaft ll extends forwardly with respect to the vehicle from a point intermediate the engine .A and the torque converter T, driving a conventional differential gear.

Figure 2 shows the engine shaft at I, mounted to rotate shaft 2 carrying clutch .plate assembly ll on splined hub ll and to rotate hollow shaft l carrying clutch plate ll assembly on splined hub ll.

Hollow output shaft 9 supports splined bevel gear I! constantly meshed with bevel gear ll afllxed to, or integral with llackshaft ll mounted on bearings I! in casing 20. Sleeve II concentric with shaft 0 is mounted to rotate about shaft 2 and has splined gear ll, roller clutch member 4 ll amxed thereto. and the rightward end is. integral with turbine element ll, the output member of the converter-unit T.

Roller clutch member 2| has external splines Ila aligning with teeth 24 and 23 of drum la which is a continuation of shaft 9. Slider II is internally splined at 22 to mesh with teeth lid and teeth 24, and externally toothed at ll. when I slider teeth 21 mesh with teeth 23 of drum la the output member II of the roller clutch F is released.

Countershaft ll with integral gears 21 and ll is driven by gear ll, reverse idler and gear- 21 from the turbine T, but gear 28 cannot transmit the power until slider II couples gear ll with teeth 23 of drum la, when drive is in reverse.

' With slider 2| placed as shown in Figure 2, the

drive is in forward. as far as gear assembly R is concerned. The torque then passes through the turbine '1 to shaft ll, roller-clutch members ll, 25, slider 28, teeth 22* and. sleeve 9.

The shaft 2 is splined to turbine impeller ll, supported by bearing II. The turbine casing Ila has attached reaction blading Ila and llb. Rotation of the impeller ll causes the enclosed fluid to move outward from the shaft center and flow in a helicoidal path about the "eye of the turbine.

Rotor ll has attached to it ring of blades ll and lie, the first receiving kinetic energy from 30. Special forms of turbine construction are not involved in this invention. The device T described herewith provides rotation of rotor 30 at varying. speeds with torque multiplication, with reference to power supplied shaft 2. Such devices are well-known in the art.

Infinitely variable speed ratios are thus provided between the shafts I and. 60 when the clutch C is engaged. Clutch F can permit the vehicle to freewheel at such time.

When clutch D is engaged, the drive is transmitted from the engine to shaft 60 at the fixed ratio of gears I2-|4, which may be a reduction, overdrive or one-to-one ratio. With clutch C disengaged, shafts 2 and I5, and turbine elements 30 40, come to-rest, roller clutch F permitting shaft 9 to overrun shaft I5, the rollers of roller clutch F idling.

It is not deemed necessary to show the details of construction of roller clutch F, since its function of permitting shaft 9 and drum to overrun shaft I has been clearly stated.

When slider 25 is in mid-position, teeth 24 are demeshed from teeth 22 of member 2|, but partial mesh with drum teeth 23 is had, so that slider 25 fully releases roller clutch F when the external controls place it in reverse drive control position. The slider is moved by fork II 3 from shaft H2 and lever III of Figure 1.

In the arrangement of Figures 2 and 3, only one servo cylinder assembly is needed to perform the work of shifting the drive between the torque converter and direct drive clutches.

The engine A is at the left, connected to the flange of shaft I, and flywheel la. The torque converter clutch C and the direct drive clutch D are grouped together at the left, and controlled by a single operating means. mounted on casing 20. This construction provides the installation of the converter unit T in a sealed housing, which simplifies the problem of protection against leakage of liquid.

Flywheel I a supports presser plates 6| and 62. the transmission shaft 2 carrying splined hub 63 and clutch disc 64 having facings 64a. Hollow shaft 9 rotates on shaft 2 and carries splined clutch hub 65 attached to clutch disc 66 having facings 66a.

Shaft 9 may drive bevel gear I2 meshed with bevel gear I4 attached to shaft 60 either through clutch D, directly driven by the engine, or through clutch C and the torque converter T.

The clutch operating mechanism provides alternate gripping of either of clutch discs I54 or 66 to shaft I, coupling shafts 2 or 9 to the engine respectively.

Fittings 61a bolted to flywheel Ia at 610 as in Figure 3 ar arranged to restrain the edges of compound disc spring 10, the inner edges of which may be shifted to the right or left by movement of bearing 'II and sleeve 12 longitudinally through eccentric yoke I3 moved by linkage external to the clutch compartment.

The shift force applied to disc spring III has fulcrum points at studs 61 and members 6141.

The presser plate 62 carries studs I5 passingthrough apertures I6 in the disc spring I0, the studs carrying fulcrum ring 11. A fulcrum portion 62a of presser plate 62 affords bearing opposite the fulcrum point of ring I1.

When bearing member II is moved to the left y yoke I3, the disc spring 10 exerts a pull on plate 6| through studs 61, against presser plate 62, thereby clamping clutch disc 66 for solid rotation with the flywheel Ia, for establishing direct drive.

When collar I2 and yoke I3 are shifted to the right, the fulcrum Ii-452a reverses the force on studs 61 and the effort is transmitted through fittings 61a to clamp the clutch disc 64 between presser plate 6| and flywheel Ia.

This disengages clutch D and couples the disc 64 of clutch C to the engine, establishing drive through turbine device T between the engine and shaft 9.

The simple rocking of lever 8| attached to eccentric shaft suffices to shift back and forth between converter and direct drive, the shaft 80 shifting yoke I3 and bearing II.

The disc spring assembly and the operating mechanism rotate with the flywheel Ia, as will be understood from inspection of Figure 3. The longitudinal motion applied through yoke 13 and bearing II attached to collar 12, shifts the disc spring I0 through center, to loading condition on either side of center, and when the eccentric 80 is moved by lever 8| to mid-position, the disc spring 10 is held on center, and both clutches C and D are disengaged,

As viewed in Figure 2, it will be seen that since yoke I3 and bearing II are in right-hand position for engaging converter clutch 64 and in lefthand position for engaging direct drive clutch 66, the eccentric 80 and external controls are required to be related about the center of. motion of the eccentric 80 so that the latter is on center at mid-position. Further, lever 8| has to rock toward the eye of the observer in Figure 2, to put the yoke I3 and bearing II in left-hand position, and away from the eye to shift them to right-hand position.

Since, in the present construction, it is desirable that the actuation system for the clutches be biased normally for converter drive, i. e., with clutch C engaged, the normal position for lever 8| will be away from the eye of the observer, and the eccentric 80 will be rocked to hold the yoke 13 and bearing II in the right-hand position, for engaging clutch C.

This is shown in Figure 4, with eccentric 80 shown rocked to the right, and servo biasing spring I02 in fully extended position.

The clutch actuation lever 8| affixed to eccentric shaft 80, outside the casing 20, occupies three control positions, one for the establishing of converter drive, a mid-position for neutral, and an opposite position for direct drive, in accordance with the designated positions in Figure 4 for the eccentric 80.

Pressure from pipe I01 in cylinder I05, therew fore shifts lever 8| to a position to put in the direct drive clutch D and release the converter clutch C.

At a point midway of the normal stroke of piston I03 in cylinder I05. a side port I09 is placed, connected to expansion chamber IIO, mounted about the cylinder I05. When air is being admitted to pipe I01 to shift the piston I03 against the action of spring I02, the uncovering of port I09 by the piston I03 causes the piston movement to dwell, until the pressure in the expansion chamber H is equal to that behind the piston I03 and in pipe I01. The release of pressure in pipe I01 permits sprin I02 to shift the piston I03 downward, but during this shift, the dwell effect of the expansion chamber i not needed, and is therefore not provided.

As described to this point, the dwell eifect at the mid-point of the piston stroke, when pressure is being admitted to pipe I01, is momenta y, that is, until the pressure in chamber I I0 is equalized, whereupon piston I03 resumes its upward travel, as in Figure '7. On the return stroke, under the force of spring I02 piston I03, the cut-off action of the edge or the piston at port I09 is such that no appreciable dwell occurs. In passing from direct to converler drive, the cushion drive effect of the fluid turbine is available for torque shock absorption. hence no dwell in clutch shifting is needed.

Figures 5, 6 and 7 show the three operating conditions of the Figure 4 construction in connection with the master valve described in Figure 8.

The air pressure from the main servo pipe I24 controlled by master valve V is delivered to pipe I0! and cylinder I05 whenever the valve is open, that is, whenever it connects the reservoir with line I24.

This air pressure is also delivered to port 95 of cylinder 92, in order to reduce the engine throttle. Cylinder 92 mounted conveniently on the vehicle, with respect to the engine throttle control, contains piston 93, and rod 94, linked to the engine throttle control mechanism. Whenever air pressure exists in line I24, the piston 93 is pressed against the action of spring 95, except when the condition of Figure 7 is met, when line pressure from I24 is exerted on both sides of piston 93, permitting spring 95 to shift piston 93 and rod 94 to the right, as in Figure 7.

Port 91 and pipe 98 connect cylinder I05 with cylinder 92 at the opposite end of cylinder 92, so that under the Figure '7 condition, there is equal pressure on both sides of piston 93. When this occurs. the spring 95 holds piston 93 at the full end of the stroke, as shown in Figure '7, so that the throttle pedal action is not interfered with.

The magnet valve V shown in Figure 8 is the master controlling valve for the clutch servo system of Figures 5, 6 and 7. It is connected through pipe I20 to a reservoir of air pressure I not shown), supplied by a conventional automatic pump common in buses and transport vehicles today. The outlet pipe I24 from valve V I eeds cylinders I05 and 92, of Figures 5 to '7, and the valve exhaust to atmosphere is shown at I34.

Valve casing 90 encloses sliding valve stem I26 in bore I 26a drilled out centrally in coil sleeve I32, and cross ported at I33 to register with exhaust port I34 leading to pipe I34a; an air valve I42 is arranged to seat in member I44 at I44a, to seal off passage of air pressure chamber I2I connectedto inlet pipe I20.

Cylindrical ring I3I embodying seat MI is set in the casing 90 and separates the servo outlet chamber I2Ia from the exhaust space about the upper portion of valve stem I26.

The stem of valve I26 projects upward into the recess of solenoid coil I35 acting as an armature for moving the valve when current is furnished from external circuits to be described. Spring I43 rests under the air valve I42 tending to hold it firm on the seat of plate I 44, sealing of! cham-- ber I2I from chamber I2Ia.

When current is supplied to'coll I 35, the armature portion I26 is drawn down by the flux fleld generated, shifting the valve I42 against the tension of spring I 43, causing a seal at I, preventing atmospheric leakage to port I34; the lower valve I42 is unseated by the abutment of valve I26, admitting compressed air from line I20 and chamber I2I to space I2Ia and outlet pipe I24.

While current flows in coil I 35, the air reservoir is constantly connected to servo feed pipe I24, and cylinders 92 and I05. When the circuit is broken, the magnetic flux field collapses in coil I35, and spring I43 shifts I42 and I28 upward, sealing off the compressed air supply from the cylinders 92 and I05.

The principal effect of current flowing in valve coil I35 is then to admit air to servo cylinder I05, to actuate the direct drive clutch, and when the external circuit is broken, spring I43 shifts the valving I42I25 to exhaust position, permitting spring of Figures 4 to 7, to actuate the converter clutch C.

The diagram of Figure 9 shows the servo device of Figures 4 to 7, the magnet valve of Figure 8, and the connection of a centrifugal governor G in the control circuit of the valve V, supplying battery current when the governor reaches a predetermined speed.

Figure 9 is a schematic diagram of a ilyball governor G driven from gear 60a of shaft 60 of Figure 2, by gear 45 on governor shaft 45a. The battery current is led to central electrode 43, slidable into and out of contact with fixed electrode 42, with increase and decrease of applied speed.

Assuming the vehicle to be driven by the turbine drive, battery current being led to governor contact sleeve 43 the latter makes contact with switch 42, at a given governor speed and through dash switch S is delivered to coil I 35 of valve V. When this circuit is completed, the master valve delivers air pressure to cylinders 92 and I05, the engine throttle lever 35 is reduced to idling position and the servo cylinder pressure moves piston I03 upward, rocking clutch actuating lever 8| upward, engaging clutch D of Figure 2, and releasing clutch C. Throttle lever 35 is pivoted to rod 94 at 35a.

When the piston I 03 uncovers port I09, air

pressure passes from cylinder I05 to line 98, and to the opposite end of cylinder 92, whereupon spring returns piston 93 and throttle connected rod 94 downward, so that the operator control of throttle 35 by rod 94 from the accelerator pedal (not shown) is restored.

In order to prevent the automatic de-throttling effect from reacting upon the foot pedal of the operator, a lost motion connection is utilized between accelerator rod 3| and rod 94.

This consists of rod 94 attached to piston 33, housed in cylinder 32 attached to accelerator pedal rod 3I, the balanced springs 34 always tending to center the cylinder 32 and piston 33 as shown in Figure 9.

The governor assembly G is driven at gear 45 by a connection from the drive of the vehicle, such as gear 60a of jackshaft 50, the gear shaft 45a carrying the conventional centrifugal weights linked to contact member 43. When centrifugal force falls off due to low speed of shaft 80, the governor return spring 45 breaks the circuit at 42-43, the valve V is returned to exhaust position so that the air pressure in cylinder I05 is exhausted, and the clutch D is disengaged by I a,seo,e77

spring I02, which thereupon engages clutch C, establishing drive in the torque converter.

This is a simple speed responsive control for the change of speed ratio. The dash switch 8 Y provides the operator with means to energise and de-energise the governor control circuit of Figure 9.

The preceding described organization of Fisure 9- and the apparatus controlled thereby provides an automatic control means for the transfer of drive between the torque converter and the direct drive afforded by clutch D of Figure 2, with interlocking means to compel the sequences for shifting a positive jaw clutch located in the direct drive position, such as described in my United States Serial Number 189,596 aforesaid, or the double friction clutch of the Figure 2 showing herein. The reactive control upon the engine throttle provides means to expedite the shift interval, and to reduce the differential of torque at the clutch assuming the vehicle torque.

In starting the drive control description herein, it is assumed that the vehicle is standing still, the engine idling, with the manually operated shift mechanism of Figures 2 and positioned for neutral or no drive.

Under these circumstances slider of Figure 2 is placed so that any residual torque on shaft I5 is not transmitted to shaft 9. The operator may warm up his engine by manipulation of the accelerator pedal, and while clutch C of Figures 1 and 2 is loaded for engagement by spring I02 of Figure 4 acting on lever 0|, no torque is trans mitted to output shaft 00, although the turbine impeller is being rotated by clutch C.

The shifting of the operator's control lever I40 of Figure 10 to forward" reciprocates rod 6 of Figure 1 and slider 25 of Figure 2 couples sleeve 2| to drum 9a of shaft 9. This shift is ordinarily done 'with the engine idling, so that the impeller The admission of air pressure to line I24 not only tends to raise piston Ill toward declutching of clutch C and clutching of clutch D, but also gives full stroke to piston 03 against the force of spring" as indicated in Figure 6. rockin throttle lever 0-0 of Figure 9-toward closed posi-' tion.' However, as soon as the-piston I00 uncovers port I00, to admit the air pressure of line I01 to the upper side of piston 03 of the auxiliarythrottle control system, the air pressure on both sides of piston 03 is the same, and spring 85 may. therefore. return the throttle mechanism to its former position.

This arrangement thereby provides a momentary tie-throttling action which reduces the torque differential to be absorbed on clutch D as that clutch is assuming the drive of the vehicle. It should be noted that the normal control of the engine throttle arm is obtained by the conventional pedal connected'to rod 3|, and that the operator, at the interval of shift, may-be endeavoring to hold agiven engine throttle'setting by ordinary manipulation of the accelerator pedal. The taking over by the governor con-" trolled mechanism of Figures 9 and 4 to 7, of the throttle control, momentarily removes 3 from the operator's pedal foot, the normal throttle res'ponse action. The admission of air pressure to line I24 by solenoid valve I05 takes the normal throttle control away from the driver's accelerator pedal foot, and the equalizing of-air' pressure on both sides of piston 93 by the passage of piston I03 upward, past port I09, restores the operator's normal foot pedal acceleration and deceleration control of engine speed. 1 a

' To prevent the awkward feelof the accelerator pedal being moved from under'the-xdrivers foot by the automatic de-throttling mechanism, the lost-motion device 3I+3233. 3l of Figure 9 is furnished, the yielding springs 34 permitting 40 of the turbine T'is incapable of delivering but a light drag torque since the centrifugal fluid 7 effect is at a. minimum at low speed.

Advancing the accelerator pedal speeds up the impeller 40 and because of the wellknown effect of circulation of fluid in turbine T, the output theautomatic action without a'pronounced varying of thefeel of the accelerator pedal under the operator's foot to any noticeable degree; The head end of rod 94 between the s'pringfl may member 30 is caused to rotate with increased speed as the engine speed is raised by the operator. the roller clutch F betweenelem'ents 2| and I0 is capable of transmitting torque during the iri-xvv Since slider 25 couples elements II and 9a,

move a limited distance, without changing the elective pressure of the accelerator pedal against the operatorsfoot. A

As far as Figure 9 in concerned, the maintaintainlng of speed of thevehicle atabove the-critical shift-over speed for whichth'e'governor G.

is designed, holds contacts43-42 of Figure 9 toterval when shaft I5 connected to the turbine output is coupled to shaft 9' coupled tothe final drive shaft 60. If the operator relax the engine throttle, the vehicle will coast, and roller clutch F will permit shaft 9 to run ahead of and free.

from shaft I5. 1 During the' above described actions, governor G of Figure 9 is being rotated at increasing speeds.-

The operator desiring to establish automatic control of the drive closes'switch S The moving gether,,so that the drive is'maintained in direct drive by clutch D, while the torque converter T stops, because clutch C is disconnected. r

Upon the falling oil in speed of the governo G, the'contact 43 moves away from'contact 42,v

breaking the circuit throughthe solenoid valve I35, and as described in connection with Figure 8,-

spring. I43 acts to seal'ofi the compressed air supply and shift the valving I42I26 to exhaust position, venting the pressure in cylinder I05, so

governor contact 43 is then capable of closing the circuit through solenoid valve' I35, admitting air pressure to 'pipe I01 for shifting the clutch C to disengaged position, and clutch D to en-' gaged position.- At the instant of shifttransition that spring I02 of piston I03 rocks the'assembly I v of Figures 4 to 7 inclusive attached-thereto to when clutch C is becoming disengaged, the engine is rotating faster than direct drive shaft 9, and" being relieved of torque by the'opening of clutch C would tend torace,puttin g a high differential of torque on the friction facings'of clutch D. To

obviate this, the engine throttle is momentarily I closed by; the structure described in connection with Figures 4. to 7 inclusive, and shown in exj temal view in Figure 9. I

the position shown in Figure 5.. This declutches clutch D and causesclutching-of clutch'C which 1 connects the drive through torque converter T" once more.

Since air pressure is simultaneously" relieved 1 in cylinder I05 and cylinder 92, theonly' possibil-.

ity ofv air pressure efiect'on'the throttle control would be the trapping of air at. a"greater-:-pres'-J 1 sure in cylinder 92 above piston. during'the interval when piston I03 was blocking port I09'-, but since such pressure is only effective toi worls withspring 95, the throttle control apparatusisJ- not thereby capable of de-throttling or of interfering with the normal throttle action.

Switch S is always available to the operator for relieving the air pressure under piston I03, and compelling the shift of drive to clutch C, so that in an emergency when converter drive is desired, the operator may always put in the multiplied torque regime of drive. In driving through heavy city traffic, this control enables the driver to drive continuously through the turbine, for frequent stop runs, avoiding wear on the shift mechanism and obviating any shift dwell action in maneuvering the vehicle.

For understanding of the forward and reverse shift mechanism, it is necessary to trace from Figure 2 to Figure .1, and to refer to Figures 10 and 11.

Slider 25 has been described as setting up one of the two trains for forward or reverse, by coupling the turbine shaft I to shaft '9 through roller clutch F, or through gears I6, 21, 20, 23, in connection with Figure 2.

In Figure 1 is shown lever II I attached to shaft II2 projecting from casing 20. Inside the gearbox, in dashed lines, is the forked lever connection to slider 25, shown in Figure 2 at I I3.

Transverse rod II4 pivoted to lever II I is attached to bellcrank II 5 pivoted on the vehicle frame, and longitudinal rod IIB from bellcrank II5 forward is connected to gear lever assembly I45 of Figure 10.

As shown in Figure 1, lever III is in "neutral position. When it is rocked about shaft II2 to the left, the slider fork I I3 of slider 25 of Figure 2 is shifted to the right, for forward drive.

Rod II 4 is therefore in tension due to a rearward force applied to rod II 6 from the lever linkage in the drivers compartment, which upon inspection of Figure 10, is understood to result from a clockwise rocking of gear lever assembly I45 for "forward selection, as marked. Rocking of I45 in the opposite direction exerts a pull on rod II6, a compression force on transverse rod.

II4 of Figure l, and a clockwise rocking of lever I II and shaft I I2, for shifting slider 25 of Figure 2 to the left for coupling gear 28 with teeth 23 of drum So, for reverse drive.

Figure 10 shows gear lever assembly pivoted on the vehicle floor-board frame at I48, having extension lever I49 integral therewith, pivoted to transverse rod IIB. Rod I451) occupies a central hole in the lever I45, and is integral with sleeve I41 and the extension to shifter ball I45a. Foreand-aft motion of lever I45 shifts rod I I6 in the same plane. The lower end of rod I45b abuts the pad I53 of lever I50, pivoted beneath the floor, the lever I50 operating switch S when the A view partly in section of switch 8" is given in Figure 10a. The casing I40c which the switch is attached to the underside of the vehicle floorboard is made of heavy insulation material, and carries cross shaft 511 to which is attached movable contact I45e mating with fixed contact I40] "wired to external lead I10. A pigtail connection rock lever I50 clockwise. This is a common form ball 5a is depressed against the action of spring I55 shrouded in sleeve I41.

The switch S connects leads I10 and 0:1 to operate the neutral-compelling mechanism of Figures 12 to 14. It is also intended to be placed in the battery circuit of Figure 9 in series with solenoid I and in parallel with switch S and governor contact 42, for operation when changing gears, to avoid inertia drag of the transmission by shifting and locking the clutch lever in mid-position.

As shown in Figure 10 a hairpin spring I40a normally separates the switch contacts, but rocking of levers I50, I40 by downward movement of shaft I b, rocks the movable contact to connect leads I10 and'llca, to energize solenoid I35 as suggested by the dashed line of Figure 14, or for energizing both solenoids I35 and I 00 of Figure 14'.

of non-grounded single-pole switch, and may take a number of different forms for executing the designated action.

Switch S operates the neutral-compelling mechanism described further in connection with Figures 12 to 14, through lever I45 pivoted to lever I50. When ball I45a is depressed the switch is made active, that is, it connects leads I10 and H011, and when the ball is released, spring I55 and hairpin springl40a return the mechanism to the positionshown in Figure 10.

The sectional view of Figure 11 shows lever I movable with the rocking shifter motion of rod H6. On the inner face of lever I40 is welded guide key I5I. Pad I53 of lever I50 moves in an arc to intersect key I5I, and notches I54F, I 54N and I54R respectively are the positions occupied by the tongue of the key I5I when the hand-lever assembly I45 is placed in the reverse, neutral and forward positions.

The lever assembly I 45 cannot be rocked through these positions until gearshift ball I45a and rod I45b are depressed sufficiently to swing lever I 50 and the notches of pad I53 clear of the key I5I.

When the new shift is accomplished, the springs I55 and I45a return the rod I45!) and notches to locking position. This interlock is to prevent accidental movement of gearlever I45 without the deliberate action by the operator, of depressing the gearshift ball I45a, so that key I5I can be swung out of the way. Switch 8 as described above, is intended to be placed in the battery circuit of Figure 9, in series with the solenoid I35 and in parallel with switch S and governor contact 42, so that when changing gear in the forward-and-reverse gearbox, the drag of the turbine may be relieved and the inertias at the point of mechanical shift may be of low values.

On the movement of the gearshift handle to any of the three positions, the ball Mia and rod I45b' are depressed against the action of spring I 55, and lever 050 is rocked, moving switch S, and energising the electrical circuit to solenoid valve V of Figure 8. This admits air pressure to servo cylinder I05 of Figure 5, and shifts the clutch lever 0| as if direct drive were goingto be established through clutch D.

At this point the system such as shown in Figure 14 may also become effective since, when the handlever operated switch 8 is engaged, a second solenoid is energized to lock and hold the piston rod I00 so that the clutch actuation of master valve V described Figures 12.to 14 illustrate a holding mechanism for latching the control mechanism for the clutches C and D in neutral position, with the circuit therefor being shown in Figure 14, and noted schematically in Figure 17.

Figures 12 and 12a show solenoid coil I60, having armature I I extended in fork I62, to intersect the motion of piston rod I00, of servo piston I03 of Figure 9, arranged to operate clutch actuating lever 8|. The rod I has two diameters, meeting at shoulder I63. Figure 12 is a vertical cross section of the lock mechanism operated by the solenoid I60, the abutment plate I65 being conveniently bolted to the casing 20 adjacent the cylinder I05 and rod I00, and affording a mounting for the solenoid I60.

The plate I65 is centrally apertured for free passage of the piston rod I00, and flaps I65a are slotted and turned from the plate I65 as shown, to act as guides for the fork I62. The fork I62 has a smaller and a larger aperture, so that when the solenoid I60 is energized, the fork will shiftto theright, the smaller aperture intersecting the path of shoulder I63 of rod I00.

As the air pressure shifts the rod I00 toward direct drive position, the shoulder I63 meets fork I62, which-is supported by plate I65 preventin the further travel of piston toward direct drive position.

This is the neutral position of rod I00, and consequently lever 8I, both clutches C and D of Figure 2 being disengaged.

When the current to solenoid I60 is cut off, return springs I66 fastened to the plate I65 and to pins I66a in fork I62, shift the armature I6I and fork I62 to the left, the release of air pressure by valve V releasing the binding force on shoulder I63 of rod I00, so that servo piston re turn spring I02 of Figure 9 is effective to return the mechanism to converter drive position.

The handlever operated circuit is shown in Figure 14. Switch S shown in Figure 10 as being operated by lever I50, rod I45!) and ball I45a, is connected by lead I'I0 to the battery, in series with the circuit through solenoid coil I35 in detail in Figure 8.

This circuit is independent from that operated by the governor of Figure 9. Since the handlever I45 will not normally be operated when the governor G would be at a speed sufficient to energise the circuit through contacts 42 and 43, there is no interference between the automatic and hand controls.

When the handlever of Figure 10 is in any one of the reverse, forward, or neutral positions, the circuit to switch S is inactive.

To facilitate understanding of the compounded circuit arrangement, Figure 14 shows the circuit of Figure 9 superimposed thereon in dashed lines.

Figure 15 presents the schematic arrangement of the controls, with particular respect to the overruling control by the operators accelerator pedal of downshift from direct drive, the control intercepting the circuit from governor G to magnet valve of Figure 8 controlling the air pressure to cylinder I05 of Figure 9, for example.

At the left of the figure, accelerator pedal 8 and lever 259 are pivoted to the floor of the drivers compartment, and lever 250 is pivoted to bellcrank I56, mounted beneath the floor. Bellcrank I56 is pivoted to throttle rod 3I which operates throttle lever 35, similarly to the construction of Figure 9.

The remainder of the system is the same as in Figure 9 except for the connections to the solenoid I35 of valve V. The lead wire from governor contact 42 instead of passing through dash switch S directly to the solenoid contact, in Figure 15, is carried forward to switch S of common construction, mounted under the vehicle floorboard.

Switch S has one contact point for lead wire I'II from 42 and S and another for lead wire I12 to the solenoid I35 of valve V. Switch S always connects leads Ill and I12 together, so that under normal operation, the driver of the vehicle with Figure 9 equipment would know no difference between it and that of Figure 15.

At beyond full throttle position of accelerator pedal 8, it encounters button I61, mounted in a floorboard fitting, loaded to occupy a normal upward position by spring I68, the rod IBIa of button being pivoted to switch lever I69 of switch S When the pedal 8 is depressed so as to stress spring I68, the operators foot on the accelerator pedal feels the added resistance of the spring, to that of the normal throttle retarding spring I57. Now if the operator so desire, the pedal 8 is pressed still further, until button rod I6'Ia rocks lever I69 far enough to operat switch S and break the circuit between leads Ill and I72.

This interrupts the current from contacts 42-43 to solenoid I35 of valve V, the valve immediately shifting to air pressure release position, as has been explained above, releasing clutch D and engaging clutch C, through th mechanism of Figures 4 to '7.

While the operator holds button depressed and switch S disconnected, the governor G is incapable of putting in direct drive through clutch D, and the drive of the engine is transmitted at full engine throttle through clutch C and the converter T to the vehicle wheels.

In operating the vehicle on heavy gradients, this provides maximum engine power at a net speed ratio reduction, or with mechanical advantage, since the turbine yields these results.

Should the operator relax the throttle so that the switch S resets itself to restor the H I--I12 circuit, the current is restored through contacts 42-43, unless the vehicle speed has fallen off below the speed at which the governor G can hold these latter contacts engaged. The governor assumes immediate charge of the drive, however, as soon as the switch S restores the circuit to solenoid I35 of valve V.

Switch S is of the same type as switch S"-, except the latter is biased by a hairpin spring to circuit disconnection position, whereas S is biased by spring I68 to circuit connection position. These switches are of common type, it being deemed unnecessary to show the internal construction thereof.

Switch S is a common two-position device mounted conveniently on the vehicle dash and may be used to eliminate the governor action entirely, and compel continuous drive through clutch C and the torque converter T. This enables the bus operators in crowded traffic to make frequent stops without being concerned with getting into direct drive, since all that is required is to place the switch in the off position, remov ing all battery current from any of the lead circuits to the relay and actuation means, so that magnet valve V is unable to admit air pressure to actuate the direct drive shift, and clutch C will remain engaged, causing turbine T to drive.

In order to facilitate the maneuverin of the remote control manual shift for forward, neutral and reverse, the present invention shows alternate means to those shown preceding in connection with Figures 10 to 14, to put the friction clutches C and D in disengaged position simultaneously.

This is accomplished through the control arrangement of Figure 17 in conjunction with the structure of Figure 16.

The gearlever 245 of Figure 16 is clamp-fitted to shaft 245 mounted in control box 241 adjacent the vehicle driver's position. The shaft may rock freely with lever 245 in the fore and aft plane,

and the fitting 248 is articulated so as to permit,

a small movement laterally of shaft 245.

The face of casing 241 is slotted at 249 in E- formation, the slot guidin the lever 245. The upper lateral tongue of the E is the forward driving position of the lever, the central tongue for neutral and the lower tongue for reverse.

The casing 24'! supports switch S mounted adjacent the portion Of lever 24-5 inside the easing, and preloaded spring 25I resting against the near' face of the switchbox and fitted in a notch 2450 of the lever, biases the lever toward the right, or tongue positions of the slot, away from the portion which permits free fore-and-aft movement. Normally, then, the lever occupies a rightward position, loaded by the spring 25I, to remain in one of the three tongues of the slot.

Striker pin 252 of switch S is arranged to operate its switch elements, as is common practice in such switches as used herein as an illustration, and when the lever 245 is moved into the free portion of slot 249, that is, toward the left, the striker pin 252 is pressed into the switch casing, actuating the contacts of switch S and thereby energising circuit I'I0I10a, which as has been previously described in connection with the diagram of Figure 14, will deliver battery current to the neutral-stop solenoid I60 of Figure 14, and also to coil I 35 of magnet valve V.

This results in admission of air to the cylinder I05 through line I24, shifting it against the compression of spring I02, while the fork stop I62 of Figure 14 is preset to lock the rod I00.

Thus when the gearlever 245 is moved sideways to the left of the notch 249, the switch S is tripped, energising the solenoid I60 and setting the lock-bar I62, so that the piston I03 of cylinder I 05 is halted in mid-position by the construction described in Figures 12 to 14.

The magnet valve V at the same time has admitted compressed air to cylinder I 05 against the return spring I02 moving the piston I03 to midposition as described above.

When the sidewise motion of the gearlever 245 is completed, the lever is then shiftable freely in either of the forward or reverse directions, to manipulate the rodding of Figure l and the shifter fork N3 of Figure 2 as described in connection with those figures; since the torque drag of the idling engine is completely removed. The halting of rod I00 in mid-position disengages both clutches C and D as described preceding The magnet valve V maintains air pressure to holdthe stop I63 of rod I00 against plate I65 of Figure 12, until the operator place the lever 245 in one of the threetongue positions of forward, neutral or reverse, because the striker pin 252 cannot release switch 8 and break the I10I'I0a circuit while the lever is in the free portion of slot 249, by virtue of the lateral spacin dime sions.

In the diagram of Figure 17, the structure of Figure 16 is shown schematically, the switch S being shown connected to wires I10 and I 10a, which by reference to Figure 14, will indicate that the arrangement works approximately the same as shown in Figures 10 and 14.

The control arrangement, however, is shown as applied to 8. Diesel power plant installation. Accelerator pedal 8, lever 259, bellcrank I56, rod 3I, lost motion connection 32-3334 and rod 94 are the same as in Fig. 15.

The accelerator pedal overruling arrangement of Figure 15 is left out of Figure 17 for the sake of clarity, although it may be superimposed thereon in the same manner that the disclosures of Figures 14 and 15 may be combined, as noted herein.

Rod 94 in Figure 17 is connected to a threearmed bellcrank 255, one work arm being linked to Diesel engine injector rack- 251 through rod 255, the rack arm increasing the injector fuel increment as pedal 8 is depressed, return spring 256 conveniently relaxing the pedal in the conventional manner. A second work arm of bellcrank 255 is joined to rod 94' attached to piston 93 of the throttle closing mechanism previously described.

The remainder of the elements shown operate exactly as previously described in this specification. The forward, neutral, reverse control for compelling full release of engine torque when shifting slider 25 of Figure 2, has been described above. This serves the very useful purpose of freeing the driving mechanism for the mechanical meshing and demeshing of slider 25, and is deemed an important contribution.

Gear lever 245 of Figure 17 is shown loaded by biasing spring 25I, the View being taken as if the observer were viewing the casing in section, from some point adjacent the reverse end of slot 249.

The actuation of striker pin 252 connects battery current from I10 to I'I0a, energising solenoid I50 and magnet valve V, as above described. It should be noted that this neutral-compelling circuit is only carrying current when the lever 245 is in transit between the positions of forward, neutral and reverse, so that current consumption for this portion of the invention is at a minimum.

The lever 250 is attached to shaft 246 and is pivoted to the mechanical shifter system similarly to lever I49 of Figure 10.

Operation The operation is described in connectionwith the structures of Figures 1 to 14 inclusive. With the vehicle standing still, engine running, the operator rocks handlever I45 of Figure 10 to forward position connecting shafts 9 and I5 through slider 25. Since the engine is idling, the flywheel Ia and connected parts have idling rotation. The vehicle being. at rest, the governor G of Figure 9 is holding the circuit of valve V open, so that noair pressure exists in pipe I24, therefore servo piston biasing spring I02 is holding in the converter clutch C, but the converter T has then only idling rotation insufficient to cause forward drive of the vehicle.

The operator in moving lever I45 of Figure 10 must depress the ball I45a in order to clear key I5I from the notch I54N of pad I53 of lever I50, which operates switch S shifting the servo piston rod I00 and clutch actuating lever ill to midposition, holding fork "I3 of the clutch spring I0 on center. This action declutches the turbine clutch C and holds direct drive clutch D disengaged. Since these responses occur before gearlever I45 can be rocked at all, the inertias of the assaerv rotating parts are low, and slider 25 couples shaft Ito roller clutch-ring of Figure 2 readily.

,Z From here on the operator need-not touch the torque converter T idles without driving the vehicle. The vehicle may be freely started and stopped by accelerator pedal and brake move- 'ments without restriction. when the road speed of the vehicle reaches a predetermined range, for example, 18 to 20 miles per hour, the governor G connects the battery circuit at 42-43 of Figure 9 and magnet valve V admits air pressure to servo cylinder I05, actuating clutch D and releasing clutchC. During. this shift interval, the engine throttle is momentarily retarded and restored by the action of the mechanism 5293-94-'-95 described above in connection with Figures to 'I.

This latter feature shortens the slip interval for the direct drive clutch D, lengthening the effective life of the clutch, as well as speeding up the transition to direct drive.

when the vehicle speed dropsbelow that for which the governor weight and spring effects maintain contacts 42-43 together, the circuit through magnet valve V of FigureB is broken, the air pressure in cylinder I5 and expansion chamber III exhausting through pipe I34a. This releases clutch D and causes clutch C to be engaged. On the return stroke of piston Ill3 of Figures 4 to 7, when port 91 is sealed, the air pressure trapped in'line 9 8 and the outer end of cylinder 52 is higher than the diminishing pressure in cylinder I05 and line I24, therefore no undesirable change of engine throttle is created by pressure on piston 93 from these latter air spaces, on the downshift.

The forwardand reverse shift system has been described above. The neutral stop action for clutches C and D has been described in detail in connection with Figures 11 to 14 inclusive.

Upon shifting to reverse from neutral, it is again necessary for the operator to depress gearlever ball I45 against the action of spring I55, and operate the neutralstopsystem of Figure-14. This assures a quick, easy, and quiet mesh of slider 25 with gear 28 and teeth 23 of drum 9a ofigigure 2, by reducing the inertias as aforesa forward and reverse, the operator also is required to depress ball l45a, and declutch both of clutches C and D. This interrupts the torque of the drive so that whatever rolling inertias there may be, cannot bind the teeth of slider 25 or jam them against disengagement.

The operation of the construction of Figure 15 is simple. and adds to the facility of control by the driver, because of the accelerator pedal overruling device incorporated in the system. The gearlever interlock described in connection with Figures l0, l1 and 14 is used with the construction of Figure 15, without interference between the mechanisms, since switch S is in parallel with circuit contacts 42-43 operated by the governor, as shown in Figure 14.

The Figure 15 construction permits the operator to downshift by depressing the accelerator pedal 3 at any time, against the action of the governor G. The utility of this feature has been explained above.

The feature of pneumatic automatic throttle reduction for the direct drive shift in the present combination is thought to be novel, its advantages having been-stated above;

\The throttle restoring arrangement described in'conne'ction with Figures -5'to 7 isfbelieved to constituteanovelsub-combinatiom The interlocking manual controls described with :respect to Figures 1.10 and 11 represent a feature for easier manipulation of the forward,

neutral and reverse selection mechanism, and the associated feature of holding theclutch' actuation means in neutral position, such that the disc spring loading device for both clutches C and D is held 'on'center, provides a new facilityin the present art. The sub-combination feature-of the expansion chamber III] for obtaining a neutral dwell during the ratio change interval is likewise believed of particularly useful character, as outlined preceding. and novl in this art.

The particular neutral stop mechanism of Figure 12 is of definite utility in releasing the gear drive from the rotating inertias of the engine- .connected power system, and the specific construction herein, in connection with the interconnected controls of Figure 14 is felt to provide utility over the prior art of definite nature.

The throttle pedal .overtravel mechanism of Figure 15 by which the operator may at any time compel the transmission ratio to be shifted from direct to reduction drive through the torque converter T is an extremely useful contribution in that it enables a vehicle operator to obtain the maximum. engine torque with the transmission at a favoring ,mechanlcal advantage, so that emergency and heavy load power requirements are better met. The sub-combination feature of the dash switch S in the above combinations extends the utility of the controls marginally, so that required continuous operation in reduction drive, of a mechanism normally operating automatically to shift to a higher ratio, is easily had, and capable of being used at any time, even when the other controls are being used. It may not be desired to use the overtravel device operated by the accelerator pedal, to compel drive in re- .60- It should be noted that in shifting out of both I duction ratio, for the operator may desire to 0perate the engine at low speed, therefore the switch S is of more than obvious utility, as a further operator control means to compel downshift.

The present invention therefore provides an accelerator pedal operated means, and an auxiliary means to compel downshift of ratio from direct to converter drive. Attention is directed also to the ability of the operator to compel neutral at any time by'depression of the gearlever extension ball I45a of Figure 10. This not only aids mesh of slider 25, and demeshing thereof, but provides the operator with means for preventing any torque from passing to the vehicle wheels, even when in that the version of the neutral-compelling control is similar to that of Figures 10, 11, and 1 2, except for structural details, and relative positionings of the parts.

In the case of the Figures 16 and 17 version. it

isnotnecessaryfortheoperatortohoidthe gearlever ball down, as in the Figure construction, when "creep may otherwise occur. In the modification arrangement, the gearlever "I need onlyberockedtooccupysomeportionofslotfll between the forward and neutral stop positions. to cause both clutches C and D to be disenga ed.

Further advantages appear above in the various text sections.

It should be understood that various changes in the form, proportion and minor details of construction may be resorted to within the scope of the appended claims, and that the present invention is now limited to the specific designs and arrangements of parts herein shown.

Having described the invention and enumerated its advantages. I now claim as new and do desire to secure by Letters Patent the following:

1. In motor vehicle controls, an engine, an engine throttle, an accelerator pedal therefor, a power shaft and a load shaft, variable transmission mechanism coupling said shafts, a lever for selecting initial drive by said mechanism, servo motor means for actuating said mechanism, control means for said motor means including a governor adapted to cause said motor means to actuate said mechanism in accordance with the speed of one of said shafts, connections between said pedal and said control means adapted to set aside the action of said governor for given move-V ment of said pedal; and additional means operative between said lever and said control means eifective to cause said control means to determine actuation of said servo motor means upon movement of said lever in selecting initial drive by said transmission mechanism.

2. In motor vehicle controls, a power shaft and a load shaft, a variable speed transmission embodying forward and reverse reduction drive means and a double clutch system alternatively operable to connect said power shaft directly with said load shaft or with said reduction drive means including a unitary actuating member shiftable between given ratio determining positions, servo motor means connected to operate said member including resilient means constantly tending to shift said member to one of said ratio determining positions, power means eifective to actuate said servo motor means against the force of said resilient means and thereby shift the said member to another ratio determining position, and a manual control for selecting the initial drive of said transmission efl'ective to control the action of said power means during the interval of initial drive selection.

3. In controls for vehicle power plants, in combination, a power plant, a throttle for said power plant, a load shaft, gearing arranged to transmit drive therebetween, a fluid driving means adapted to couple said power plant to said gearing, alternate driving means coupling said power plant directly with said load shaft, coupling mechanism operative to connect said fluid driving means or to connect said alternate driving means to said power plant and having a single operating member which in one position couples one of said driving means and in another position alternately couples the other, a power device effective to actuate said member for said alternate connection of said means, a unitary control for said device, a speed responsive governor driven by said load shaft, a driver controlled member controlling said throttle, mechanism coacting with said control operated by said governor, and a connection from said driver controlled member to said mechassaevv anism effective when the driver controlled memberismovedpastfullthrotfle, tocircumventth'e action of said governor upon said control.

4..In motor vehiclepowercontrols, an engine an engine throttle, a vanaflbl'e speed connectin driving and en shafts, alternatively actuable clutches for direct or reduction drive in said on, a member for actuating said clutches, fluid pressure operated servo motor means effective to actuate said clutches through positioning of said member, valve means controlling said servo motor means, a governor normally operative to shift said valve in accordance with the speed of one of said shafts, an accelerator pedal connected to increase and decrease said throttle opening over a given range'of movement, connecting means between said pedal and said valve means effective when said pedal is moved to beyond full throttle position to direct fluid pressure to said servo motor means and cause shift of said clutches from direct to reduction drive in said transmission, while rendering said governor ineflective to select actuation of said clutches, and resistance means interposed in the path of motion of said pedal, effective at beyond full throttle position thereof to provide added force to be overcome by the driver's foot.

5. In powercontrol equipment for motor vehicles, in combination, a power shaft and a load shaft, a variable speed ratio drive therebetween, embodying two coupling clutches one of which couples said shafts directly the other of which couples them indirectly, mechanism for shifting the engagement of said clutches alternately be tween direct and indirect drive, consisting of a common loading means 'eifective upon either of said clutches to hold one or the other in driving engagement, and a single shifting means adapted to transfer the loading of said loading means from one clutch to the other; actuation means operative on said shifting means, including a shiftable member, a control for said mechanism, and controllable'stop means made effective by said control and acting upon said member for holding said mechanism in such position that both said clutches are thereby held disengaged and said loading means rendered inefl'ective.

6. In vehicle power controls, a power shaft and a load shaft, driving means coupling said shafts arranged to provide direct or reduced ratio drive therebetween, auxiliary power means arranged to actuate said driving means, including a member moved by said auxiliary power means to various speed ratio determining positions, one of which positions disconnects all drive by any of the elements of said driving means for placing the 1 drive in neutral, loading means effective to bias the positioning of said member toward one or another of two ratio determining positions and effective to resist holding in said neutral position, control means for said power means operative to position said member in neutral against the action of said loading means, and mechanism operated by said control means and effective to stop the movement of said member at the said neutral position.

7. In ower drive controls, an engine driving a motor vehicle through a power shaft directly connected to the engine, a driven shaft, 0. variable speed transmission coupling said shafts, a governor driven by one of said shafts, actuating means arranged to establish selected speed ratios of said transmission, control means acting upon said actuating means subject to the speed effect of said governor and to the positioning of said pedal for selection .of driving speed ratio. a hand control operative to select the initial driving ratios .of said transmission when starting the vehicle from rest, and a means linking the movement of said hand contr with said'control means where- ,sion, and'a device worked by saidmanual control by for given tra'nsitional movement of the hand control, the positioning of .said pedal andthe "speed effect of said governor on said control means are both rendered ineffective.

8. In variable speedratio transmission c'om; trols, an engine, a power shaft driven by the engine, a load shaft, driving means adapted to couple said sh'afts directly, at reduced speed ratios and in reverse ratio, auxiliary power means arranged to actuate said driving means, an electrical control system operative to manipulate said power -means for establishing direct and reduction ratios in said driving means, a mechanical system effective to control said driving means for forward and reverse drive, a single control for said mechanical system, and a switch made operative by movement of said control toward either forward or reverse drive position to render said direct and said reducedratio coupling inactive.

9. In power controls for motor vehicles, a driving and a driven shaft, driving mechanism interposed between said shafts including selectively operated gearing and alternatively operable clutches for direct drive and reduced drive, servo motor means arranged to operate said clutches, a circuit comprising a source of electrical energy, a control switch, a magnetically operable valve arranged to control said servo motor means, an electrically operable stop mechanism for holding the said means in a predetermined position for non-actuation of either of said clutches, wiring connecting said source, said switch, said valve and said device, the circuit being arranged to operate the valve and the said device when said switch is moved to connecting position, and a manually operated selector for said gearing adapted to connect said switch during predetermined selection movement thereof.

10. In motor vehicle power controls, a power shaft and a load shaft coupled by a variable speed transmission which includes alternatively driving clutches engageable and adapted for bein held engaged by a single spring means, a shifter means effective to transfer the loadingof said spring means from one clutch to the other, actuating means for said shifter means normally biased for energising one of said clutches, auxiliary power means operative upon said actuating means for overcoming the normal biasthereof and effective to shiftsame and said shifter means to an alternate. position in which the said one of said clutches is disengaged and the other of said clutches energised, and a separate control subject to the will of the operator at all times capable of placing the said actuating and said shifter means in a third position such that both clutches are held disengaged.

11. In motor vehicle power controls, a power shaft and a load shaft coupled by a variable speed transmission which includes alternatively driving clutches engageable and adapted for being held engaged by a single spring means, a shifter means effective to transfer'the loading of said spring means from one clutch to the other, actuating means for said shifter means normally biased for energising one of said clutches, auxiliary power means operative upon said actuating means for overcoming the normal bias thereof and effective to shift same and said shifter meansto an alternate position in which the said one of said clutches "means adapted tocompel the shifting of said actuating and said shifter means to a third position in which both said clutches are held disengaged when the said manual control means is moved between predetermined positions.

=12. In motor vehicle power controls, driving and driven shafts, a driving mechanism connecting said shafts including alternatively selected direct and reduction drive establishing devices and gearing having a sliding member adapted to select initial geared drlvethrough said mechanism;control means for said mechanism including a manual shift lever connected to shift said member to selective gear drive positions of said gearing, a

mounting for said lever permitting longitudinal and lateral motion, a supporting casing for said lever and said mounting equipped with an'arcuate,

' longitudinal guide slot having laterallegs at selective gear drive positions of said lever and a lateral leg atthe neutral position thereof ,biasing means tending to holding the lever in one of said legs of said slot, and a device made operative by lateral motion of said lever against said spring, and effective while said lever occupies the longitudinal portion of said slot, to prevent actuation of said driving mechanism for establishing either direct or reduction drive.

13. In automatic controls for motor vehicles, an engine. an engine throttle, an accelerator pedal controlling said throttle between full and idling throttle positions, a power shaft and a load shaft, a variable speed ratio transmission mechanism coupling said shafts including direct and reduction drive establishing means including a dual friction clutch assembly with clutches alternately engaged by movement of a single operating member, auxiliary power means adapted to actuate I the said member, a control system operative upon said-auxiliary power means comprising a governor driven by one of said shafts tending to cause said power means to actuate said member so as to establish the direct drive means and thereby change ratio to direct drive, and connecting means between said system and said pedal effective when said pedal is moved past full throttle position to circumvent the action of said governor and compel drive in reduction by said mechanism by said reduction drive means clutch thru actuation of said member by saidpower means.

14. In automatic controls for motor vehicles, an engine, speedcontrol means for said engine, an accelerator pedal for said control means, a power shaft and a load shaft, a variable speed transmission coupling said shafts at direct and reduction speed ratios, ratio control means for said transmission embodying a manual lever for establishing initial drive thereby and auxiliary power operated, automatically controlled means forestablishing selected forward speed ratios, automatic control mechanism therefor vcomprising a governor driven by one of said shafts arranged to select the ratios determined by said power operated means and a connection between said mechanism and said pedal effective to set aside the action of the govan engine, speed control means for said engine, an accelerator pedal for said control means, a power shaft and a load shaft, a variable speed transmission coupling said shafts at direct and reduction speed ratios, ratio control means for said transmission embodying a manual lever for establishing initial drive thereby and auxiliary power o erated, automatically controlled means for establishing selected forward speed ratios,

automatic control mechanism therefor comprising a governor driven by one of said shafts arranged to select the ratios 'determined'by said power operated means and a connection between said mechanism and'said p dal elective to set aside the action of the governor when placed in a given position by said pedal, a separate connection between said ratio control means and said lever operative to energise said power operated means when said lever is moved toward aratio establishing position, and a neutral stop device worked by said separate connection moved by said lever adapted to prevent the power operated means from establishing either direct or I reduced drive in said transmission during said energizing action.

16. In variable. power controls, an engine, a

said valve and said device arranged in a circuit for operating the said valve and the said device when said switch is moved to circuit connecting position, a manually operated selector for said gearing adapted to connect said switch during predetermined selection movement thereof, and automatic controls responsive to the speed of one of said shafts eifective to shift said valve to establish drive by one or the other 01' said clutches, during intervals when said selector is stationed for disconnecting said switch.

18. In power controls for motor vehicles, a

. power shaft and a load shaft, a variable speed ratio drive between said shafts including forward and reverse driving means and two coupling clutches one of which couples said shafts directly the other of which couples them indipower shaft driven by the engine, a load shaft,

driving means including engageable clutches adapted to couple said shafts directly, or to coupie them at reduced speed ratios and in reverse ratio, power means arranged to cause engagement and disengagement of said clutches, an electrical control system operative to regulate the action of said power means for establishing selective engagement of said clutches, a mechanical shift system for said driving means effective to establish initial forward or reverse drive. a single lever control for said mechanical system, a switch made operative by movement of said lever within a given range toward either forward or reverse drive position to render the clutches for coupling said direct and said reduced ratios inactive, and automatic controls for said power means responsive to the speed of. said load shaft for providing shift of said clutches from reduction to direct drive with increase of speed thereof.

1'7. In power controls, a driving and a driven uhaft, driving mechanism interposed between said shafts including a selectively operated gearing unit providing forward and reverse drive and having alternatively operable clutches providing rectly at reduction ratio, mechanism for shifting the alternate engagement of said clutches consisting of a common loading means effective upon either of said clutches, including a disc-shaped spring effective to'hold one-or the other of said clutches in driving engagement, a single shifting means adapted to transfer the loading action of said spring from one clutch to the other; fluid pressure actuation means operative on said shifting means, inc1uding a shiftable member movable between limiting end positions, a control for said mechanism with controllable stop means made effective by '40 said control for acting upon said member to hold direct and reduced drive, fluid servo motor means arranged to cause operation of said clutchea a said mechanism in a mid-point position such that both said clutches are held disengaged and said spring is rendered ineffective, control means operative to establish forward or reverse drive between said shafts by said forward and reverse driving means, a lever arranged to select forward or reverse drive by said last-named contol means, and a connecting control between said lever and said stop means operative to energise the latter at a neutral drive position when the lever is positioned between its forward and re-. verse selecting positions.

HANS O. SCHJOLIN.

said loading means 

